Fluid-operated motor

ABSTRACT

A fluid-operated motor of the radial valve type, the motor having a hydraulically balanced and actuated valve-seating mechanism equally responsive to reversed motor-operating fluid flow and a positive circulation lubrication system providing controlled lubrication at all wear points during operation of the motor.

United States Patent 1 1 3,572,983

[ Im'CmQY "98 Mfnerfnofl [56] References Cited Mmmlml's UNITED STATESPATENTS [2]] Appl. No 874,757 [22 Filed Nov. 7,1969 2,956,512 10/1960Brundage 418/132 [45] Patented Man, 1971 3,270,683 9/1966 lvlcDermott...418/61 [73] Assignee Germane Corporation 3,289,542 12/1966 Fikse 418/61Minneapolis Minn 3,391,608 7/1968 Huber 418/61 3,452,543 7/1969 Goffetal 418/61 3,452,680 7/1969 White,Jr. 418/61 Primary Examiner-Carlton R.Croyle Assistant Examiner-Wilbur .l Goodlin 541 FLUID-OPERATED MOTOR 8Claims, 9 Drawing Figs.

[52] US. Cl 418/61, ABSTRACT: A fluid-operated motor of the radial valvetype,

418/13 1 the motor having a hydraulically balanced and actuated valve-[51] Int. Cl F0lc 1/02, seating mechanism equally responsive to reversedmotor- FOlc 19/08 operating fluid flow and a positive circulationlubrication [50] Field of Search 418/61 system providing controlledlubrication at all wear points dur- 131, 132 ing operation of the motor.

file

Patented March 30, 1971 4 Sheets-Sheet l rvw INVENTOR.

HUGH 1.. 44 015 44077 4770EA/EV Patented March 30, 1971 3,572,983

4 Sheets-Sheet 2 O 67 *mlln' g 46 108 INVENTOR.

' HUGH A. MQDEQIJOTT F1155 Patented 'March so, 1971 3,572,983

4 Sheets-Sheet 3 INVENTOR.

HUGH L. M "DEE/14077 ATTOPUEI/ Patented March 30, 1971 4 Sheets-Sheet 4INVENTOR.

HUGH 444 3591400 FUJtD-GPERATEDMOTDR SUMMARY OF THE INVENTION Thisinvention relates to a fluid-operated motor of the radial valve typeand, more particularly, relates to a fluid-operated motor of the radialvalve type having a hydraulically balanced and actuated valve-seatingmechanism and positive lubrication to all moving parts therein.

BACKGROUND OF THE INVENTION Although fluid-operated motors and pumps ofthe radial or disc valve type have been known and utilized in the past,many difficulties have been experienced with the valve and valve seatingof these motors. For example, ports of a radial valve acting under orconveying pressurized fluid to a valve plate tend to be urged away fromthe valve plate which they confront and, diametrically opposed to thepressure ports on the radial valve, are exhaust ports which do not havecorresponding forces urging the valve away from the valve plate.Consequently, there is a tilting or cocking force on the valve as itrotates. Although this problem is capable of solution, as may be seen inUS. Pat. No. 3,270,683 issued to H. L. McDermott on Nov. 6, I966entitled Porting Arrangements for Balancing Valve of Fluid PressureDevice", the solution to the tilting or cocking force was made at theexpense of loss of bearing surface between the valve and the valveplate. Obviously, without adequate bearing surface, wear is acceleratedand corresponding inefficiencies result. A radial valve having adiameter increased sufficient to compensate for the loss of wearingsurface in the valve of US. Pat. No 3,270,683 may be provided, but in sodoing, the diameter of the motor is correspondingly increased, limitingthe applications in which the motor may be utilized.

Besides the tilting force on the valve as described above, there areother forces acting on the valve. Typically, the radial valve of a motorof the type described herein, must be driven in synchronization with thedisplacement mechanism. Since the displacement mechanism is connected tothe output shaft, oftentimes the valve is subjected to the thrust loadson the output shaft transmitted to the valve by the mechanicalconnections between the shaft and the valve. This thrust load on thevalve separates the rotating valve from the stationary valve plateduring operation. Obviously, this would cause a leakage between thehighand low-pressure passages, and possibly, a total malfunction of thevalve and therefore of the motor could result.

Conventional spring-loaded or hydraulically actuated valveseatingmechanisms are inadequate to offset or compensate for all of the forcesacting on the valve. Among the problems experienced with conventionalvalve-seating mechanisms, and their corresponding valves, arelubrication between the stationary and rotating elements and, problemsexperienced from the inability to totally lubricate the motor whenconventional valve-seating mechanisms and valves are utilized in a motorof the type herein described.

In motors heretofor available, lubrication was approached in a randomfashion. For example, leakage through high-pressure interfaces suppliedthe lubrication to various bearings, spline connections and betweenother parts moving at relatively different rotational speeds. Since thislubrication was random, in that some high-pressure interfaces allowedleakage and others did not, lubrication was oftentimes inadequate. Inthe manufacture of high-precision hydraulic motors for operation undervery high torque requirements at very low speeds, controlled lubricationmust be provided assuring proper lubrication to each of the movingparts.

With these comments in mind, it is to the elimination of these and otherdisadvantages to which this invention is directed.

OBJECT S OF THE INVENTION An object of this invention is the provisionof a new and novel fluid-operated motor of the radial valve type ofsimple and inexpensive construction and operation.

Another object of this invention is the provision of a new and improvedfluid-operated motor having controlled lubrication of all moving partstherein.

Still another object of this invention is the provision of a new andnovel fluidbperated motor having a hydraulically balanced andhydraulically responsive valve-seating mechanism to maintain the valvein proper seated relation relative to the valve plate and to overcomethrust exerted on the valve as a result of thrust on the output shaft.

A further object of this invention is the provision of a fluidoperatedmotor having a radial valve which is balanced in such a way as toprovide optimum wear characteristics in a valve having a minimumdiameter thereby maintaining the overall diameter of the motor at aminimum.

These and other objects and advantages of this invention will more fullyappear from the following description made in connection with theaccompanying drawings wherein like reference characters refer to thesame or similar parts throughout the several views.

DRAWINGS OF THE INVENTION FIG. I is a longitudinal sectional view of thefluid-operated motor of this invention.

FIG. 2 is an end view taken along the line 2-2 of FIG. 1.

FIG. 3 is sectional view taken along the line 3-3 of FIG. 1.

FIG. 4 is a sectional view taken along the line 4-4 of FIG. 1.

FIG. 5 is a sectional view taken along the line 5-5 of FIG. I.

FIG. 6 is an enlarged partial sectional view taken along the line 6-6 ofFIG. 2.

FIG. 7 is an enlarged sectional view taken along the line 7-7 of FIG. 1.

FIG. 8 is a partial enlarged sectional view taken along the line 8-8 ofFIG. 2.

FIG. 9 is a partial enlarged sectional view showing a detail of thevalve seating mechanism and the lubrication system.

DESCRIPTION OF THE INVENTION Referring now to FIG. I, the fluid-operatedmotor of this invention is indicated in general by reference numeralIt), and comprises several main portions joined to form a generallycylindrically shaped motor or pump. An end cap ll, which may beconstructed from cast aluminum, includes fluid inlet opening 12 andfluid outlet opening 13, each of which is internally threaded to receivea hydraulic line. It should be noted that fluid inlet and outlet may bereversed in the event opposite direction of rotation of the output shaftis desired. The end cap contains valve Id which is rotatably mounted inopening 15 for rotation of valve 314, about the longitudinal axis In ofmotor 10. Valve 114 includes a transverse valve plate confront ingsurface l7 as well as a plurality of fluid-conducting passages whichwill be discussed hereinbelow.

Stationary valve plate portion 18, having a transverse valve confrontingsurface 19, is positioned adjacent end cover plate ll. Valve platesection 118 includes a plurality of axially oriented fluid-conductingpassages in fluid communication with valve is and its fluid-conductingpassages; the detail and relation therebetween will be discussedhereinbelow. Valve plate section I8 includes a valve drive receivingopening 21 which is axially oriented and adapted to receive a valvedrive which is substantially oriented for rotation along axis id, but ata slight angle thereto. The valve plate section may be constructed frompowdered metal.

A displacement mechanism or gerotor set is indicated at referencenumeral 22; and is positioned adjacent valve plate section Ifsandwiching valve plate section l8 between end cover plate ii anddisplacement mechanism 22. It should be noted that the displacementmechanism is in fluid communication with the axially orientedfluid-conducting passages in valve plate section 28. The displacementmechanism will be discussed in detail hereinbelow.

Displacement mechanism sealing plate portion 23 is positioned adjacentthe displacement mechanism and includes an axially oriented opening 24adapted to receive a drive member for rotation substantially along axisl6 but at a slight angle thereto. Displacement mechanism sealing plateportion 23 is stationary and sandwiches displacement mechanism 22between sealing plate portion 23 and valve plate 18. It may beconstructed of powdered metal or steel as desired. 7

A generally cylindrically shaped shaft housing 25, having an axial bore26 therein concentric with axis 16, is connected adjacent displacementmechanism sealing plate portion 23. The shaft housing is typicallyconstructed of cast aluminum.

A front end cap 27 is connected to shaft housing by a plurality ofaxially oriented bolts 28. The front end cap includes an axial opening29 adapted to receive an output shaft. A shaft seal 30 is positioned incounter bore 31 and shaft seal 32 is positioned in annular groove 33.The end cap may be constructed from steel.

End cap ll, valve plate 18, displacement mechanism 22, displacementmechanism sealing plate 23 and shaft housing 25. are connected by aplurality of axially extending circumferentially spaced bolts 34,forming a generally cylindrically shaped motor body or frame.

Output shaft 35 is positioned in shaft housing 25 for rotation withinbore 26 about axis l6. The output shaft includes a loan naled portion 36adapted to be connected to the drive chain of a mechanism eitherdirectly coupled or through a sprocket, gear, or pulley, as appropriate.Thrust bearing 37 is seated between shaft 35 at the journaled portion 36thereof, sandwiched between shaft shoulder portion 38 and the front endplate 27. Forward roller bearing assembly 39 and rearward roller bearingassembly 40 are positioned within housing 25 to receive shdt 35. Rearthrust bearing 41 is seated within circumferential groove 42 ofdisplacement mechanism maling plate 23. Shaft 35 has an internal,axially oriented receiving bore 43.

Referring now to the displacement mechanism or gerotor set 22, theconstruction thereof is best shown in FlG. 3. Gerotor set 22 comprisesan outer. substantially ring-shaped member 44- having a generallycircular, axially oriented and concentric opening 35 therein. Outer ringmember 44 includes a plurality of axially oriented arcuate openings,circumferentially spaced about axially oriented opening 45, and denotedby reference numerals 46. Each arcuate opening is typically slightlymore than 180. Rolls 47 are rotatably mounted in openings 46 forrotation about a longitudinal axis parallel with axis 16 but spacedradially outwardly therefrom. Rolls 47 form a plurality of internalteeth with which externally toothed star gear member 48 mates. Star gearmember 48 has a plurality of external teeth 49 numbering one fewer thanthe internal teeth or rolls 47 of ring member 44. The star gear memberis eccentrically disposed in ring member 44 and orbits relative theretoabout motor axis 16 and rotates on its own axis 50. During this orbitalmovement, external teeth 49 of the star gear member mesh with ringmember rolls or teeth 47 in sealing engagement and with a rolling actiontherebetween, to form expanding and contracting cells 51 which are equalin number to the number of teeth of ring member 44. Cells 51 are influid communication with passages in valve plate 18. The outer ringmember is typically constructed from powdered metal and the rolls from aselected hardened steel alloy.

A line of eccentricity of displacement mechanism 22 is indicated by thecenterline at reference numeral 52 and is defined as that line whichpasses through motor axis 16 and the star gear member axis 50. Thefunction of a gerotor set is well known and will not be described indetail herein. it should be noted that the outer ring member maycomprise integral teeth providing a sliding action between the innerstar gear member and the outer ring member.

Valve plate 18 is best seen in FIG. 4. it includes a plurality offluid-conducting openings 53 in fluid communication with cells 51 ofdisplacement mechanism 22. Fluid-conducting openings 53 are adapted toconvey fluid under pressure or exhaust fluid to and from cells 511.Valve plate 18 is stationary. it is typically constructed of powderedmetal. Openings 53 are axially oriented circumferentially spaced, andpositioned radially outwardly from axis 16 of motor ill}. Theycorrespond in number to the number of cells in the displacementmechanism. The valve plate and the valve-sealing plate sandwiches thegerotor set inbetween to enclose displacement mechanism cells 51 in amanner well known in the art.

Valve-balancing ports 54 are shown positioned between fluid-conductingopenings 53. Each valve-balancing port includes a bearing surface 55therein and a fluid-receiving groove 56 adapted to receive fluid underpressure to provide balancing of the valve at the valve plateconfronting surface l7 thereof.

Referring now to H6. 5, the valve 14 is shown mounted in end cap ll forrotatable movement about axis 16. Valve plate confronting surface 17confronts and mates with valve plate surface l9. A plurality of valveports are included in valve 14. Assuming fluid inlet pressure is at portl2, valve fluid pressure ports are indicated by reference numeral 57 andexhaust ports are indicated by reference numeral 58. Obviously, valvepressure ports 57 are in communication with inlet port 12 and valveexhaust ports 58 are in fluid communication with exhaust port 13. in theevent reverse direction of output shaft 35 is desired, inlet and outletfluid to and from ports 52 and l3 is reversed; port 12 becomes theoutlet port and port 13 the inlet port. Accordingly, valve port 57 isthe exhaust port and valve port 58 is the pressure port. I

During operation of the valve relative to the valve plate, certain ofvalve ports 57 are in registry or fluid communica tion with certain ofvalve plate openings 53 at the same time that valve ports 58 are inregistry with other of valve plate openings 53. The relationtherebetween will be discussed more completely hereinbelow.

Star gear member 48 of displacement mechanism 22 is connected to valve Mwhich is synchronized therewith. It should be noted that the exhaustpassages correspond in numberto the number of teeth 49 of star gearmember 48. Of course, the number of pressure passages also correspond tothe number of teeth 49. in this way fluid is supplied to and exhaustedfrom cells 51 of the displacement mechanism synchronized with therotation of the star gear member.

The connection between the star gear member and the valve is provided byvalve drive 59. The valve drive includes a splined portion 69 matingwith an internal spline 61 in the star gear member and a splined portion62 which mates with a mating internal spline 63 in valve 14.

Star gear member 453 is connected to output shaft 35 by main drivemember 64. The main drive member is inserted within shaft 35 at bore 43and includes a splined portion 65 which mates with an internal spline 66within bore 43. Also included in main drive member 64 is a splinedportion 67 which mates with internal spline 61 of the star-gear member48. It should be noted that, since the main drive member and valve drivemember are each slightly angulated relative to axis 16 that the splinesmust be so designed to accommodate this angulation caused by theeccentricity of star gear member 4% as it rotates on its axis 50 andorbits about axis 16 of the motor. The configuration or tooth form ofthe splined portions is well known in the art and will not be discussedherein. A spacer 68 is positioned in a counter bore 69. The diameter ofspacer 68 approximates the minor diameter of spline 65 in order to allowfluid to circulate around the splined connections.

' The valve-seating ring is indicated by reference numeral 79 in PEG. 1.The valve-seating ring detail is best shown in FIG. 7. Valve-seatingring 70 is circular and typically constructed of powdered metal. Acentral bore 7ll is provided and the valveseating ring is mounted in endcap ill concentric with axis 16 utilizing rearwardly proiecting integralring portion 72 which is inserted into a corresponding and mating groove73 in end cap Ill. It should be noted that axial movement ofvalve-seating ring relative to end cap it is allowed by the assembly.Groove 73, in end cap Ill, includes a plurality of axially extendingbores 7 2- adapted to receive pin '75 which projects rearwardly fromring 72 of valve-seating mechanism 763. Pin

75 acts as a rotation preventing and aligning element. A spring 76surrounds pin 75 and is caged between projecting portion 72 and bore 74.The pins and springs are utilized as needed; typically two pins and twosprings are needed. In this manner, the seating ring is urged axiallyoutwardly from end cap l1 into contact with valve l4 at thevalve-seating ring confronting surface 77 thereof. The valve-seatingring 74) includes valveconfronting surface '78 which mates with surface77 in sealing engagement relative thereto, yet allowing relativemovement therebetween.

Valve-confronting surface 78 of valve-seating ring 70 is made up of aseries of lands and grooves each concentric with axis 16 of motor ill).Inner bearing land 80 is followed by first inner groove iii. A pluralityof inner notches 32 are provided causing groove 81 to be in fluidcommunication with notches 52. Inner sealing land 83 separates firstinner groove 81 from second inner groove 84, providing sealingtherebetween. Inner middle bearing land 35 is provided and is followedby middle groove 36. Outer middle bearing land 87 is followed by secondouter groove '88. Outer sealing land 89 seals outer grove 90 from secondouter groove 88. Outer bearing land 91, in com-' bination with inner andouter bearing lands 85 and 87 respectively, provides the bearing surfaceon which the valve-seating mechanism confronting surface of valve 14 issupported. A plurality of outer notches 92 are provided placing outergroove 90 in fluid communication therewith. A plurality of axiallyprojecting openings 93are circumferentially spaced at predeterminedintervals interrupting and communicating with second inner groove 84,middle groove 86 and second outer groove $8.

As best seen in FIG. 3, inner sealing ring 94 is provided and seated inend cap ll at the connection between valve-seating ring assembly 70 andend cap 11. Ring 94 is constructed from resilient material such asTeflon. Sealing ring d4 is seated between end cap transverse surface 95and the rear facing transverse surface '96 of valve-seating ring 70.Axial movement of valve-seating ring 70 causes surfaces 95 and 96 to beurged axially inwardly and outwardly. Seal 94 effectively seals at alltimes during the axial movement.

Outer sealing ring 97 provides a seal between transverse surface 95 ofend cap ll and surface 96a of valve-seating mechanism '70. Sealing ring97 is resilient, typically Teflon, and when surfaces 95 and 96a areaxially apart as well as when surfaces 95 and 9601 are urged togetherfrom the action of hydraulic fluid during operation of the motor.

A first fluid containing volume 98 is defined by the valve 14,valve-seating mechanism 70, inner sealing ring 94, end cap ll, and innersealing land 83. A second fluid-containing volume lid is defined byvalve l4, valve-sealing mechanism 70, outer sealing ring 97, end cap ii,and outer sealing land 89. Assum ing the fluid pressure inlet is at port12, first volume 98 contains operating fluid under pressure and volume99 contains fluid under exhaust. In the event it is desired to reversemotor rotation, the fluid inlet and outlet are reversed and thefunctions of volumes 9% and 99 are reversed with 99 becoming pressureand 9f becoming exhaust.

The controlled lubrication system is best described by assuming thatfluid under pressure enters port 12 into volume 98. Lubrication systemfluid flow first contacts metering notch rue positioned in valve Mconfronting surface 78 of valveseating mechanism '70. Metering notch msallows a predetermined amount of fluid under pressure to be placed influid communication with middle groove 86 of the valve-seating ring 7%.Middle groove 85 is, in turn, in fluid communication with a plurality ofvalve-circulating system passaged 101 which allow fluid to be conductedtherethrough into contact with valve drive mating splines 62 and 63 andmating splines as and fill thereby lubricating the spline connection.Circulation fluid flow is through bore 24 in shaft 35 providinglubrication at the spline connection 67 and bi and the spline connection65 and as. Lubrication fluid flows around spacer 63 into transverseopenings W2 and M33 which communicate with bearings Lubrication tothrust bearing '37 is through the surface between the bearing 39 and theshaft 35. hearing spacer 104 is provided to separatebearings 3 9 and db.The bearing spacer includes opening res allowing lubrication fluid topass therethrough into angulated housing lubrication system passage 1%.The displacement mechanism sealing plate includes a lubrication systempassage W7 positioned to registry with passage W5 of the housing 25.Displacement mechanism 22 includes lubrication system passage lfld inregistry with passage m7. Valve plate it) includes lubrication systempassage M9 in fluid communication with passage W8. Lubrication fluidflows into branch passage lit) in end cap 11 at which pointspring-loaded pressure responsive ball 111 is unseated for seat Illa(Exhaust pressure is slightly less than lubrication fluid pressure.)Bore 11112 encloses spring M3 which is contained therein by bolt 1M andat seat lllla, caging the spring and allowing pressure to unseat theball. Lubrication passage l15 connects bore 112 with secondfluid-containing volume 99. Lubrication fluid is exhausted from themotor since volume 99 is in fluid communication with outlet port 13. Itshould be noted that the shaft-supporting housing includes a drain plug116 which is in fluid communication with the lubrication system. ifdesired, fluid may be exhausted directly from the motor by opening thedrain port.

Assuming that operating fluid under pressure enters at port 13, meteringnotch 1% allows fluid flow from volume 99 through outer sealing land 89into middle groove 86 which is in fluid communication with valvecirculation system passages llll. Fluid circulates around the valvedrive and the main drive members as above and into branch passage ill).As may be seen in FIG. l, the fluid under pressure in volume 9% incommunication with passage urges ball llll into seat 111a. Withreference now to FIG. 6, fluid flow is then through branch I17 unseatingball 118 from seat 118a. Spring 119, which is caged in bore 120 by boltlZl, allows lubrication fluid pressure to overcome the spring-biasingforce. Fluid flow is into bore 220 and then into passage 122. Withreference to FIG. 9, it should be noted that passage 122 is in fluidcommunication with volume 98 allowing the lubrication fluid to flowthrough port l2 which is the exhaust port for reverse rotation.

OPERATION OF THE lNVlENTION The general operationof a fluid-operatedmotor of the gerotor or roller gerotor type is well known in the art andwill not be described in detail herein. However, for purposes ofdescribing the operation of the invention as it pertains to afluid-operated motor, a brief description of the operation of agerotor-type fluid-operated motor will be included.

For a given direction of shaft rotation, fluid under pressure entersport l2 into first volume 98. Fluid flows from volume 98 into passages57 in valve 14 into passages 53 in registry therewith and then intodisplacement mechanism cells Sl on one side of the line of eccentricity52. The cells expand and simultaneously urge inner star gear member 48to rotate about its axis 50 and orbit about motor axis lb.Correspondingly, fluid exhausted from cells on the other side of theline of eccentricity 52 is conveyed through appropriate passages 53, invalve block 18, into passages 58 in valve 14 and exhausted from thefluid-operated motor through port l3. As the star gear member rotates itcauses valve 14, through valve drive member 59, to synchronously rotateabout axis .116 providing timing between the displacement mechanism andthe valve so that fluid enters appropriate cells on one side of the lineof eccentricity and is exhausted from cells on the other side of theline of eccentricity. The inner star gear member is connected line ofeccentricity, and passages 57 become the fluid exhaust passages. Fluidis conveyed through the valve plate 18 passages 53 timed to the rotationof the star gear member 48 of displacement mechanism 22. Cells 51 areexpanded and contracted as for rotation described above, except thatfluid flow from the contracting cells is through valve passages 57 intofluid-containing volume 98 and then exhausted from the motor throughpassage 12.

The specific operation of valve-seatingmechanism 70 is best described byassuming that the operating fluid inlet is at port i2. Fluid is conveyedinto fluid-containing volume 98 under pressure of, for example, 2,000p.s.i. This fluid is contained within this volume by valve 14, innersealing land 83, valve-seating mechanism 70 and inner sealing ring 9 inorder to prevent leakage at valve confronting surface 19 and valve plateconfronting surface 17 between passages 57 which are under pressure andpassages 58 which are under exhaust (approximately l p.s.i.), valve 14must be maintained in sealing engagement with valve plate l8. Valveplate confronting surface 37 of valve 34 bears against valve confrontingsurface E9 of valve plate 1%. The fluid under pressure influid-containing volume provides the force urging surfaces 17 and 19,respectively, into tight sealing engagement. However, since valve 14rotates relative to stationary valve plate 18, the forces urging valve14 against plate 1% must be carefully controlled in order to accomplishsealing without preventing rotation therebetween. To this end fluidunder pressure flows through notches 82 in valve-seating ring mechanism70 into first inner groove bi placing a predetermined area of the valveseating mechanism confronting surface 77 of valve 14 under the influenceof the operating fluid urging valve 14 axially into contact with plate38. Inner sealing land 83 prevents the fluid under pressure from actingon a larger area of surface 77. in this manner, the proper amount offorce is constantly supplied during operation of the fluid operatedmotor.

it should be noted that valve-seating mechanism 70 is biased axiallyforwardly by a plurality of springs 76. At the time of starting motorl0, springs 76 urge valve-seating mechanism 70 axially forwardly intocontact with valve 14 engaging sealing land 33 thereagainst. Valve 14,in turn, is urged axially forwardingly into contact with valve plate 18thereby preventing leakage between ports 57 and 58 at the startup. itshould be noted that inner sealing ring 94 prevents fluid under pressure(approximately 2,000 p.s.i.) from leaking from volume 98 into thelubrication system containing fluid-at lubricating pressure(approximately 100 p.s.i.). Further, sealing ring 94 is resilient andseals regardless of the axial position of valve-sealing mechanism 70thereby preventing loss of efficiency caused by leakage from thehigh-pressure area to the low-pressure area.

The operation of the valve-seating mechanism for shaft rotation reversedfrom the description immediately above is as follows. Fluid entersvolume 99 under pressure of approximately 2,000 p.s.i. from port l3.Fluid flows through outer notches 92 into outer. groove 90 of thevalve-seating mechanism 70. In this manner, fluid under pressure isallowed to act upon valve M at the valve-seating mechanism confrontingsurface 77 thereof. Valve 14 is urged axially forwardly into tightsealing contact with valve plate 18 at the valveconfronting surface 19thereof. Outer sealing ring 97 prevents fluid under pressure fromflowing out of fluid-containing volume 99 into the lubrication system.Outer sealing ring 97, since it is resilient, seals in all axiallyoriented positions of valve-seating mechanism 70. Valve passages 58provide fluid under pressure to the displacement mechanism cells andpassages 57 exhaust the fluid from the collapsing cells.

Since valve 14 is urged against the stationary valve plate 18 at surface19 thereof, sufficient bearing surface must be provided in order toprevent undue wear. Further, valve balancing must be provided to preventtilting or cocking of the valve from the unbalanced forces on eitherside of the line of eccentricity. To this end, balancing ports 54 areprovided. Each balancing port includes a fluid-receiving groove 56 whichreceived fluid under pressure from valve 14. Assuming that fluidcommunication with cells which are contracting. At such times as thecells on one side of the line of eccentricity are being pressurized bycommunication with predetermined valve passages, diametrically oppositepassages are not being pressurized by the valve but the valve passages57 contain fluid under pressure acting upon the valve plate. Thebalancing port receives this fluid thereby providing relief and preventscocking or tilting of the valve relative to the valve plate. it has beenfound that fluid receiving groove 56 which surrounds bearing island 55adequately balances the valve yet allows adequate bearing surfacetherebetween. This eliminates the necessity of increasing the diameterof valve and valve plate surfaces 17 and 19, respectively, whichconfront each other. In the event fluid under pressure enters port l3),the operation is the same as described above except that passages 57 and58 conduct fluid under reversed conditions.

in isolating high pressure areas-from low pressure areas, certainportions of the motor could be isolated from all fluid flow.

Consequently, except for the provision of a controlled lubricationsystem, inadequate lubrication and a corresponding decrease inefficiency would result. Positive controlled lubrication is achieved byutilizing metering notch which is located transversely in valve 14across the valve-seating mechanism confront surface 77 thereof. Notch100 places a predetermined amount of fluid approximately proportional tothe differential pressure existing existing between volume Q8 and thelubrication system in fluid communication between volume 98 and middlegroove 86 of valve seating mechanism '70. Metering notch 100 is of aconfiguration requiring substantial pressure to urge oil therethroughfrom volume 98 which contains fluid under pressure. This pressure causesthe metering notch to carry fluid across inner sealing land 03 intocontact with second inner groove 84 and middle groove 86. However, sincethe second inner groove and middle groove and 86, respectively, are influid communication with the lubrication system there is not sufficientpressure to urge fluid from the circulation system through notch 100past outer sealing land 89 into volume 99 containing fluid under exhaustpressures. Therefore, second inner grcmve 84 and middle groove 86contain fluid only available for circulation through the lubricationsystem of the motor. Metering notch continuously provides lubricationfluid in predetermined amounts and at predetermined pressure to thesecond inner and middle grooves. Second inner and middle grooves are influid communication with, and interrupted by, a plurality of openings 93which, in turn, are in fluid communication with valve passages i0l.There is constant fluid communication between valve passages 101 andgroove 86. Lubrication system pressure is slightly greater than exhaustpressure. For example, if the circulation system pressure is at 1,050p.s.i., the exhaust pressure is at 1,000 p.s.i. Notch 100 will not allowfluid flow between these pressure differentials.

Lubrication fluid flow is through passages 101 around spline connections62 and 63 of valve drive member 59. Flow continues through opening 21 invalve plate 18 into the spline connections 60 and 61 of star member &8.At this point, the spline connections 60 and 61, as well as 67 and 61 ofthe main drive member 64, are lubricated. Flow of lubrication systemfluid is forwardly of the motor into bore 33 of shaft 35. The splineconnections 65 and 66 between main drive member 6 3 and shaft 395 islubricated by oil which next flows around spacer 68 into lubricationpassages E02 and W3 lubricating forward bearings 39. Forward thrustbearing 37 is lubricated by lubrication system flow around bearing 39 atthe surface of shaft 35. Lubrication system flow provides forlubrication of bearing 40 and thrust bearing ill. Flow is forward andrestricted by close meter fit between the shaft-housing bore 26, thebearing spacer and shaft 35. in this manner, the main portion oflubrication system fluid is made available to the spline connection 65and 66. Lubrication system flow is then through bearing separatoropening 105 into angulated passage lltlb in the shaft housing.Lubrication system flow is through passage 107, 1108 and 109 in thedisplacement mechanism sealing plate 23, displacement mechanism 22 andvalve plate 1%, respectively, into branch 116 in end cap lll. At thispoint, ball llll is unseated, since it is acted upon only by fluid underexhaust pressure. Consequently, lubrication fluid flows into volume 99and is exhausted from the motor through port 113. The lubrication fluidcannot unseat ball llfi since it is acted upon by fluid under pressurein volume 98 through passage 122.

in the event it is desired to change the direction of rotation of themotor shaft, the fluid under pressure enters port 13 into volume 99 and,therefore, metering notch 100 allows the fluid under pressure to flowpast outer sealing land 89 into second outer groove 88 and middle groove86. Metering notch 1% cannot carry fluid from middle groove so intovolume 9d which contains fluid under exhaust since the pressuredifference will not allow fluid flow therethrough. Circulation for thelubrication system is as described above except that circulation fluidflow from passage 109 in valve plate 18 is into branch M7 in end cap ll,unseating ball 118 from seat 118a, allowing fluid flow into bore 120which is in fluid communication with passage 122. Passage 122 is influid communication with volume 98, the volume containing fluid underexhaust which is at a slightly lower pressure than the lubricationfluid. it should be noted that fluid under pressure in volume 99 isconveyed through passage 115 into bore 112 preventing ball ill frombeing unseated from seat lllla thereby forcing fluid flow into branchM7.

in the event it is desired to place fluid operated motors of the typedescribed herein in series operation, inlet and outlet ports i2 and 13are at substantial pressure. Therefore, the case drain is utilized bysimply removing drain plug H6 and connecting the outlet to a reservoir.The lubrication fluid flow is the same as described hereinabove exceptthat the return passages, providing an outlet for the lubrication fluid,are not utilized. Valve M and valve seating ring 70 are eachhydraulically balanced and biased as described hereinabove in the seriesoperation.

From the foregoing, it will be seen that l have provided a new and novelfluid-operated motor of the radial valve type having simple andinexpensive construction and operation and including provision, in ahighly sophisticated motor utilizing high-tolerance manufacturingtechniques, for proper valve balancing and seating as well as controlledlubrication throughout the working parts of the motor. Provision hasbeen made for efficiently seating the valve against the valve plateallowing the valve to rotate without leakage between the pres sure andexhaust ports at the valve plate. Further, controlled lubrication hasbeen provided through a metering notch allowing fluid under pressure tocirculate through the lubrication system in one direction withoutdecreasing the efficiency of the motor and without sacrificing thereversibility feature of the motor. New and novel resilient sealingbetween the high and low pressure containing volumes of the motor hasbeen provided so that there is efficient separation of fluid at alltimes. Proper bearing surface has been provided for the valve relativeto the valve plate whereby the valve is supported utilizing a minimumdiameter valve and valve plate.

lclaim:

l. A reversible fluid-operated motor of the radial valve typecomprising:

a generally cylindrically shaped housing;

'a valve-housing portion connected to said cylindrically shaped housing,said valve-housing portion including fluid inlet and outlet ports;

an output shaft mounted in said housing for rotation about alongitudinal axis;

a displacement mechanism having expanding and contracting cellsresponsive to motor operating fluid;

a main drive member connecting said displacement mechanism with saidoutput shaft whereby movement generated in said displacement mechanismin response to motor-operating fluid is transmitted to said outputshaft;

a valve mounted in said valve-housing portion for rotation about itslongitudinal axis, said valve having a plurality of fluid-conductingpassages, alternate of the passages being in fluid communication withinlet fluid and other alternate passages being in fluid communicationwith outlet fluid, said valve positioned in said valve-housing portionseparating inlet fluid from outlet fluid, said valve having avalve-seating mechanism confronting surface and an opposed valve plateconfronting surface transverse to the longitudinal axis thereof;

a valve plate positioned between said displacement mechanism and saidvalve, said valve plate having a plurality of fluid-conducting passagestherein in fluid communication with valve passages and displacementmechanism cells, the passages adapted to conduct operating fluid to andfrom displacement mechanism cells in a predetermined sequence, saidvalve plate having a transverse valve-confronting surface in tightsealing engagement with the valve plate confronting surface of saidvalve;

a valve drive member connecting said valve with said displacementmechanism providing synchronous rotation therewith;

a valve-seating mechanism, having a transverse valve-confrontingsurface, mounted in said valve-housing portion for axial movementtherein and with the valve-confronting surface adjacent thevalve-seating mechanism confronting surface of said valve, saidvalve-seating mechanism biased urging the valve-confronting surfacethereof in tight sealing cngageme nt with the valve-seating mechanismconfronting surface, said valve-seating mechanism separating inletoperating fluid from outlet operating fluid at the valve-confrontingsurface thereof, the valve-confronting surface including;

an annular inner groove in fluid communication with operating fluid;

an annular outer groove in fluid communication with operating fluid; and

a middle bearing land separating and sealing the inner groove from theouter groove and separating and sealing inlet fluid from outlet fluidwhereby inlet operating fluid in communication with one of said innerand outer grooves, which fluid is under pressure and positioned betweensaid valve seating mechanism and said valve, urges said valve in sealingengagement with said valve plate.

2. The fluid-operated motor of claim 1 wherein said valveseatingmechanism lands and grooves are substantially circular and concentric.

3. The fluid-operated motor of claim 2 wherein said valveseatingmechanism valve-confronting surface includes;

an inner bearing land adjacent said inner groove;

an inner sealing land adjacent said inner groove and sandwiching saidinner groove between said inner bearing land and said inner sealingland;

a second inner groove adjacent said inner sealing land and sandwichedbetween said inner sealing land and said middle bearing land;

a second outer groove adjacent said middle bearing land;

an outer sealing land adjacent said second outer groove,

sandwiching said second outer groove between said middle bearing landand said outer sealing land; and

an outer bearing land adjacent said outer groove and sandwiching saidouter groove between said outer sealing land and said outer bearingland.

4. The fluid-operated motor of claim 3 including:

a substantially circular inner sealing ring therefrom between with saidinner bearing land and positioned radially inwardly concentric saidvalve-seating mechanism and said valve housing; and

a substantially circular outer sealing ring positioned radiallyoutwardly from said outer bearing land between said valve-seatingmechanism and said valve housing, said inner and outer sealing rin'gsadapted to separate inlet and outlet operating fluid.

5. The fluid-operated motor of claim 4 wherein said inner and outerrings are resilient and provide sealing of inlet and outlet operatingfluid during axial movement of said valve seating mechanism.

6. The fluid-operated motor of claim l wherein said valve plate includesa plurality of valve-balancing ports spaced between the fluid-conductingpassage thereof, each of said valve-balancing ports including bearingsurfaces therein having an operating fluid-receiving groove therearound.

7. The fluid-operated motor of claim 1 wherein:

said cylindrically shaped housing includes a motor lubrication systemadapted to provide lubrication fluid to said motor including a pluralityof fluid-conducting passages in fluid communication with the motorportions in communication with lubricating fluid and with the outletport thereof;

said valve includes a plurality of lubrication fluid-conducting passagesin fluid communication with the lubrication system passages in saidhousing;

said valve-seating mechanism valve confronting surface thereof includesa middle groove positioned in said middle bearing land, the groove influid communication with the plurality of lubrication fluid conductingpassages in said valve whereby fluid under pressure is conducted fromsaid middle groove through said motor for lubrication thereof and thenconducted outwardly from said motor through the lubrication system,passages thereof to the outlet port thereof; and

a fluid-metering notch providing fluid conducting means from the fluidinlet port of said motor to the middle groove of said valve-seatingmechanism valve-confronting surface.

8. The fluid-operated motor of claim 7 including:

a first lubrication fluid conducting passage in fluid communication withsaid inlet port disposed in the valve housing portion thereof;

a second lubrication fluid conducting passage in fluid communicationwith said outlet port disposed in the valvehousing portion thereof, eachof which first and second lubrication fluid conducting passages are influid communication with the lubrication system fluid conducting passagein said housing; and

a pressure-responsive check valve interposed in each of said first andsecond lubrication fluid conducting passages whereby fluid from thelubrication system fluid conducting passages of said housing flowstherefrom through the outlet port of said motor and whereby inlet fluidflows from the inlet port of said motor though said valve.

E12 ULIITZD STATES FATE??? OFEE'E'CE M (Jemima-1T3 CGRZZECTEON PatentNo. 3 572, 983 Dated March 30, 1971 Inventor(s) Hugh L. McDermott It iscertified that error appears in the above-identified paten and that saidLetters Patent are hereby corrected as shown below:

In the drawing, Sheet 1, Figure l, the reference numeral 98 should beapplied to the fluid containing volume defined between the fluid portopening 12 and the valve member 14 and the reference numeral 99 shouldbe applied to the fluid containing volume between the fluill portopening 13 and the valve member 14. Column 1, line 29, "wearing" shouldread bearing- Column 5, line 44, after "and and before "when surfaces9S"insert sea1s-; line 71, "bore 24" should roadie-opening 24 and. bore43; line 75, "bearings 39 should read -bearing 39--. Column 7, line 18,"100" should read -l00O-; line 47, "100" should read --l050-. Column 8,line 69, "bearings 39'f should read -bearing 39-.

Signed and sealed this 12th day of October, 1971.

(SEAL) Attest:

' ROBERT GOTTSCHALK Acting Commissioner of Patent EDWARD M.FLETCHER,JR.Attesting Officer

1. A reversible fluid-operated motor of the radial valve typecomprising: a generally cylindrically shaped housing; a valve-housingportion connected to said cylindrically shaped housing, saidvalve-housing portion including fluid inlet and outlet ports; an outputshaft mounted in said housing for rotation about a longitudinal axis; adisplacement mechanism having expanding and contracting cells responsiveto motor operating fluid; a main drive member connecting saiddisplacement mechanism with said output shaft whereby movement generatedin said displacement mechanism in response to motor-operating fluid istransmitted to said output shaft; a valve mounted in said valve-housingportion for rotation about its longitudinal axis, said valve having aplurality of fluidconducting passages, alternate of the passages beingin fluid communication with inlet fluid and other alternate passagesbeing in fluid communication with outlet fluid, said valve positioned insaid valve-housing portion separating inlet fluid from outlet fluid,said valve having a valve-seating mechanism confronting surface and anopposed valve plate confronting surface transverse to the longitudinalaxis thereof; a valve plate positioned between said displacementmechanism and said valve, said valve plate having a plurality offluidconducting passages therein in fluid communication with valvepassages and displacement mechanism cells, the passages adapted toconduct operating fluid to and from displacement mechanism cells in apredetermined sequence, said valve plaTe having a transversevalve-confronting surface in tight sealing engagement with the valveplate confronting surface of said valve; a valve drive member connectingsaid valve with said displacement mechanism providing synchronousrotation therewith; a valve-seating mechanism, having a transversevalve-confronting surface, mounted in said valve-housing portion foraxial movement therein and with the valve-confronting surface adjacentthe valve-seating mechanism confronting surface of said valve, saidvalve-seating mechanism biased urging the valve-confronting surfacethereof in tight sealing engagement with the valve-seating mechanismconfronting surface, said valve-seating mechanism separating inletoperating fluid from outlet operating fluid at the valve-confrontingsurface thereof, the valve-confronting surface including; an annularinner groove in fluid communication with operating fluid; an annularouter groove in fluid communication with operating fluid; and a middlebearing land separating and sealing the inner groove from the outergroove and separating and sealing inlet fluid from outlet fluid wherebyinlet operating fluid in communication with one of said inner and outergrooves, which fluid is under pressure and positioned between said valveseating mechanism and said valve, urges said valve in sealing engagementwith said valve plate.
 2. The fluid-operated motor of claim 1 whereinsaid valve-seating mechanism lands and grooves are substantiallycircular and concentric.
 3. The fluid-operated motor of claim 2 whereinsaid valve-seating mechanism valve-confronting surface includes; aninner bearing land adjacent said inner groove; an inner sealing landadjacent said inner groove and sandwiching said inner groove betweensaid inner bearing land and said inner sealing land; a second innergroove adjacent said inner sealing land and sandwiched between saidinner sealing land and said middle bearing land; a second outer grooveadjacent said middle bearing land; an outer sealing land adjacent saidsecond outer groove, sandwiching said second outer groove between saidmiddle bearing land and said outer sealing land; and an outer bearingland adjacent said outer groove and sandwiching said outer groovebetween said outer sealing land and said outer bearing land.
 4. Thefluid-operated motor of claim 3 including: a substantially circularinner sealing ring therefrom between with said inner bearing land andpositioned radially inwardly concentric said valve-seating mechanism andsaid valve housing; and a substantially circular outer sealing ringpositioned radially outwardly from said outer bearing land between saidvalve-seating mechanism and said valve housing, said inner and outersealing rings adapted to separate inlet and outlet operating fluid. 5.The fluid-operated motor of claim 4 wherein said inner and outer ringsare resilient and provide sealing of inlet and outlet operating fluidduring axial movement of said valve seating mechanism.
 6. Thefluid-operated motor of claim 1 wherein said valve plate includes aplurality of valve-balancing ports spaced between the fluid-conductingpassage thereof, each of said valve-balancing ports including bearingsurfaces therein having an operating fluid-receiving groove therearound.7. The fluid-operated motor of claim 1 wherein: said cylindricallyshaped housing includes a motor lubrication system adapted to providelubrication fluid to said motor including a plurality offluid-conducting passages in fluid communication with the motor portionsin communication with lubricating fluid and with the outlet portthereof; said valve includes a plurality of lubrication fluid-conductingpassages in fluid communication with the lubrication system passages insaid housing; said valve-seating mechanism valve confronting surfacethereof includes a middle groove positioned in said middle bearing land,the groove in fluid communication with the pLurality of lubricationfluid conducting passages in said valve whereby fluid under pressure isconducted from said middle groove through said motor for lubricationthereof and then conducted outwardly from said motor through thelubrication system passages thereof to the outlet port thereof; and afluid-metering notch providing fluid conducting means from the fluidinlet port of said motor to the middle groove of said valve-seatingmechanism valve-confronting surface.
 8. The fluid-operated motor ofclaim 7 including: a first lubrication fluid conducting passage in fluidcommunication with said inlet port disposed in the valve housing portionthereof; a second lubrication fluid conducting passage in fluidcommunication with said outlet port disposed in the valve-housingportion thereof, each of which first and second lubrication fluidconducting passages are in fluid communication with the lubricationsystem fluid conducting passage in said housing; and apressure-responsive check valve interposed in each of said first andsecond lubrication fluid conducting passages whereby fluid from thelubrication system fluid conducting passages of said housing flowstherefrom through the outlet port of said motor and whereby inlet fluidflows from the inlet port of said motor though said valve.